CN102959262B - There is the isolation belt wheel of the ability of surmounting and vibration damping ability - Google Patents
There is the isolation belt wheel of the ability of surmounting and vibration damping ability Download PDFInfo
- Publication number
- CN102959262B CN102959262B CN201180031578.8A CN201180031578A CN102959262B CN 102959262 B CN102959262 B CN 102959262B CN 201180031578 A CN201180031578 A CN 201180031578A CN 102959262 B CN102959262 B CN 102959262B
- Authority
- CN
- China
- Prior art keywords
- clutch
- spring
- input
- decoupler
- bracket
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000013016 damping Methods 0.000 title description 5
- 238000002955 isolation Methods 0.000 title description 4
- 238000007789 sealing Methods 0.000 claims description 16
- 239000008041 oiling agent Substances 0.000 claims description 3
- 238000010276 construction Methods 0.000 claims description 2
- 125000006850 spacer group Chemical group 0.000 abstract description 15
- 238000000034 method Methods 0.000 abstract description 5
- 230000015572 biosynthetic process Effects 0.000 abstract description 3
- 238000004804 winding Methods 0.000 description 16
- 239000008186 active pharmaceutical agent Substances 0.000 description 6
- 239000000463 material Substances 0.000 description 4
- 230000007704 transition Effects 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 229920001971 elastomer Polymers 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 239000000806 elastomer Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000007634 remodeling Methods 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/12—Friction clutches with an expansible band or coil co-operating with the inner surface of a drum or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/76—Friction clutches specially adapted to incorporate with other transmission parts, i.e. at least one of the clutch parts also having another function, e.g. being the disc of a pulley
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
- F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
- F16D7/022—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with a helical band or equivalent member co-operating with a cylindrical torque limiting coupling surface
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
- F16H2055/366—Pulleys with means providing resilience or vibration damping
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49826—Assembling or joining
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Operated Clutches (AREA)
- Pulleys (AREA)
Abstract
There is provided a kind of decoupler, it has input hub, output link, overrunning clutch and at least one spacer spring.Rotating power passes through overrunning clutch, spacer spring be delivered to output link along predetermined sense of rotation from input hub.Additionally provide a kind of method for the formation of decoupler.
Description
Technical field
Present invention relates in general to one and there is the isolation belt wheel (isolationpulley) surmounting (overrunning) ability and vibration damping ability.
Background technique
Disclose in US patent application publication No.2010/0140044 and 2007/0037644 and surmount decoupler.Surmounting decoupler although this and meet very much its expection object, still existing in this field providing the needs surmounting decoupler reversing isolation.
Summary of the invention
This part provides the overview to present disclosure, instead of its characteristic four corner comprehensively open.
In one form, this instruction provides a kind of decoupler, and this decoupler comprises input hub, output link and clutch and isolated system, and described clutch and isolated system have overrunning clutch and torsional isolator.Described overrunning clutch has clutch input structure, clutch spring, bracket and clutch export structure, and described clutch input structure is connected in described input hub regularly to rotate together with described input hub.Described clutch spring is formed by spring thread and has multiple coil and the first end being installed on described bracket.Described bracket is non-rotatably installed on described input hub and is oriented the axial end of the spring thread forming the described first end of described clutch spring against described clutch input structure.Described clutch export structure has clutch surface.Rotating power for expansion is against described clutch surface, thus is passed to described clutch export structure from described input hub along the first sense of rotation by the described coil structure of described clutch spring.The described coil structure of described clutch spring for shrinking, thus allows described clutch export structure to surmount described input hub along described first sense of rotation.Described torsional isolator comprises input queued switches part, exports actuator and at least one spring, and at least one spring construction described is along described first sense of rotation transmitting torque between described input queued switches part and described output actuator.Described input queued switches part is connected in described clutch export structure to rotate together with described clutch export structure.Described output link is connected in described output actuator to rotate together with described output actuator.At least one layout of spring described of described torsional isolator is at the radial outside of described clutch spring.
In another form, the instruction of present disclosure provides a kind of method for the formation of decoupler.The method can comprise: the clutch spring around overrunning clutch installs torsion spacer spring with one heart, described overrunning clutch is drivingly attached to input hub, and described overrunning clutch is configured to along predetermined sense of rotation transmitting rotary power between described input hub and described torsion spacer spring; And by described decoupler balance to predetermined rotation non-equilibrium state, make when not having torsional load by described decoupler carrying, described decoupler rotates uneven, and, when the torsional load carried by described decoupler increases to predetermined torsional load, the rotation imbalance of described decoupler reduces.
In another form, the instruction of present disclosure provides a kind of decoupler, and it has input hub, output link, overrunning clutch and at least one spacer spring.Rotating power passes through described overrunning clutch along predetermined sense of rotation from described input hub, be delivered to described output link by described spacer spring.
The structure of the decoupler of this mode can have many merits, depends on the final structure of decoupler.Such as, the overall dimension of overrunning clutch can be reduced relative to prior art, make the cost of overrunning clutch lower.As another example, relatively large spring can be integrated in decoupler, the different spring rate that (compared with using the decoupler of multiple spring) can have cost advantage like this and/or provide the spring structure relying on other easily not obtain.Also can obtain other not in the advantage that this expresses.
According to description provided herein, other application will become apparent.Description in content part of the present invention and concrete example only have no intention for exemplary purpose to limit the scope of the present disclosure.
Accompanying drawing explanation
Herein contained accompanying drawing only for exemplary purposes but not be intended to limit the scope of the present disclosure by any way.Part similar or identical in all different accompanying drawings is with reference character identical all the time.
Fig. 1 is the rear perspective view of the example decoupler constructed according to the instruction of present disclosure;
Fig. 2 is the exploded perspective view of the decoupler of Fig. 1;
Fig. 3 is the longitudinal cross-section view of the decoupler of Fig. 1;
Fig. 4 is the partial rear view of the decoupler of Fig. 1, it illustrates bracket, clutch spring and is connected in the clutch input structure on input hub;
Fig. 5 is the partial perspective view of the decoupler of Fig. 1, it illustrates the second end of the clutch spring be arranged on spring bracket; And
Fig. 6 is the partial longitudinal section view with the decoupler of support member constructed in an alternate manner;
Run through the multiple views in accompanying drawing, corresponding reference character indicates corresponding component all the time.
Embodiment
See the Fig. 1 to Fig. 3 in accompanying drawing, the decoupler according to the constructed of present disclosure is referred to by reference character 10 entirety.Decoupler 10 can comprise input link 12, clutch and isolated system 14, output link 16 and damper 18.
See Fig. 2 and Fig. 3, input link 12 can have input hub 20, and input hub 20 has hub component 30 and annular shoulder 32.Hub component 30 can be configured in any desired way decoupler 10 is attached to live axle DS.In the concrete example provided, multiple through hole 36 is formed through hub component 30 and is configured to receive the threaded fastener (not specifically illustrating) extended there through, and this threaded fastener is threadedly coupled on live axle DS.It being understood that input hub 20 and live axle DS can have the feature allowing the center line of input hub 20 to aim at exactly with the spin axis of live axle DS.In the concrete example provided, the hole 38 in hub component 30 and the engagement formation between the guide portion 40 of live axle DS are the angle described center line being positioned to expectation relative to described spin axis.Annular shoulder 32 can comprise the surface 44 of circumference extension and the radial surface 46 extended.
The damper 18 be not shown to scale can comprise the torsional vibration damping device of any type, comprises and utilizes viscous shear, tangential springs power and/or frictional force to cushion the damping device of torsional vibration.In the concrete example provided, damper 18 utilizes tangential springs power and comprises damper input link 22, resilient member RI and inertia member IM.Damper input link 22 can be the discreet component that can be attached to input hub 20 in any suitable manner.In the concrete example provided, damper input link 22 is welded on input hub 20, and it allows the operation by comprising forging to form input hub 20, and damper input link 22 can be formed by steel plate materials.But it being understood that if damper input link 22 is formed discretely with input hub 20, then other different coupling arrangements be can use, one or more threaded fastener and/or interference fit comprised.Damper input link 22 can have leg 48 and arm 50, leg 48 can from a part---such as annular shoulder 32---for input hub 20 radially, arm 50 can be connected to the far-end of leg 48 and can extend forward from leg 48, thus arranges with one heart with input hub 20.Resilient member RI can comprise can connect (such as bonding or frictionally joint) to the elastomer on damper input link 22 and inertia member IM.Inertia member IM can be loop configuration, and its size can be configured in the known any mode in this field the torsional vibration eliminating preset frequency at least in part.
Clutch and isolated system 14 can comprise overrunning clutch 54 and torsional isolator 56.In the concrete example provided, overrunning clutch 54 comprises clutch input structure 60, bracket 62, clutch spring 64, clutch output link 66 and spring bracket 68, and torsional isolator 56 comprises input queued switches part 70, at least one spacer spring 72 and exports actuator 74.
See Fig. 2 to Fig. 4, clutch input structure 60 can be connected on annular shoulder 32, and clutch input structure 60 can be rotated jointly with input link 12.Clutch input structure 60 can have bearing surface 80, and this bearing surface 80 can extend from the radial extensional surface 46 of annular shoulder 32.
Clutch spring 64 can be formed by the spring thread of suitable shape of cross section, and can comprise the multiple spiral windings 86 be arranged between first end 88 and the second end 90.First end 88 radially inwardly can extend from adjacent spiral winding 86, and correspondingly can comprise the first linearity range 94 and the second linearity range 96, First Transition region 98 and the second transition region 100.First linearity range 94 radially inwardly can extend from described adjacent spiral winding 86 one-tenth first angle, and the second linearity range 96 radially inwardly can extend from the second angle that a described adjacent spiral winding 86 one-tenth is larger.First linearity range 94 can be attached to a spiral winding 86 of described vicinity by First Transition region 98, and the second linearity range 96 can be attached to the first linearity range 94 by the second transition region 100.See Fig. 2 to Fig. 5, the second end 90 can comprise the tang 104 that can be parallel to the central axis extension forming spiral winding 86 around it.
Get back to Fig. 2 to Fig. 4, bracket 62 can be incorporated in annular shoulder 32 around, and bracket 62 can be configured to support clutch spring 64 when rotating power is passed to clutch spring 64 from clutch input structure 60.Bracket 62 can by the material be applicable to---such as, steel or plastics---formed, and flange portion 110, sleeve part 112, groove 114 and bracket contacting wall 116 can be comprised.Flange portion 110 can be the loop configuration with front surface 118 and rear surface 120, and front surface 118 can abut the radial extensional surface 46 of annular shoulder 32, and rear surface 120 can abut an adjacent spiral winding 86 of clutch spring 64.In the example provided, abut clutch spring 64 rear 120 part in the shape of a spiral so that the outline of the spiral winding 86 with clutch spring 64.Sleeve part 112 can be the loop configuration axially extended from flange portion 110.The size of sleeve part 112 can be configured to be accommodated in the spiral winding 86 of clutch spring 64, to support one or more spiral winding 86 and/or to remain the first end 88 of bracket 62 and clutch spring 64 around common axis of rotation line.Groove 114 can be configured to the first end 88 receiving clutch spring 64, and can extend through the circumference of sleeve part 112 and preferably extend through bracket contacting wall 116.Bracket contacting wall 116 can abut clutch input structure 60, and if groove 114 extends through bracket contacting wall 116, then the axial end 126 forming the spring thread of clutch spring 64 can also abut the bearing surface 80 of clutch input structure 60.In the concrete example provided, clutch input structure 60 is straight pin (therefore the cylindrical shapes of bearing surface 80), and is arranged so that what the centre line C L C(of clutch input structure 60 and end face perpendicular to axial direction 126 obtained relative to axial end 126) spaced apart with this vertical center line CLD radially outwardly at the some place that the vertical center line CLD of the spring thread forming clutch spring 64 is crossing with axial end 126.Centre line C L D can be arranged between the spin axis of centre line C L D and decoupler 10 by the structure of which, it can contribute to limiting the line forming clutch spring 64 in some cases.But it being understood that other structures of clutch input structure 60 and clutch spring 64 are also in the scope of present disclosure, therefore to illustrate and the concrete example that describes is interpreted as not limiting the present invention disclosed herein herein.
If needed, bracket 62 can be configured to non-rotatably be connected on input link 12.In the concrete example provided, as shown in Figure 4, the flange portion 110 of bracket 62 has notch, to receive clutch input structure 60, thus makes the first end 88 of bracket 62(and therefore clutch spring 64) remain predetermined direction relative to clutch input structure 60.
Although bracket 62 has been described to have the flange portion 110 being formed as continuous print loop configuration, but should be understood that bracket 62 can alternatively be formed as discontinuous loop configuration.In this respect, flange portion 110 can be formed as having radial slot (not shown), thus provides larger circumference compliance monitoring for bracket 62.Substitute as another kind, bracket 62 can be press-fitted on annular shoulder 32, thus is connected on input link 12 by bracket, to rotate thereupon.
Simply see Fig. 6, support member 130 can be connected on input hub 20, exits from groove 114 to prevent the first end 88 of clutch spring 64.In the example provided, support member 130 is formed by steel and is press-fitted into input hub 20, but should be understood that and can use other joining methods.Such as, support member 130 can comprise outside snap ring or thrust washer (not shown), and it can by rights---and such as, to be incorporated in correspondingly configured circular groove in (not shown)---be attached to input hub 20.
Get back to Fig. 2 and Fig. 3, clutch output link 66 can comprise circumferential extended structure, and this circumferential extended structure can be arranged around the spiral winding 86 of clutch spring 64.Clutch output link 66 can comprise clutch surface 140, and this clutch surface 140 can be engaged by the spiral winding 86 of clutch spring 64, as will be hereafter discussed in detail.
See Fig. 2,3 and 5, spring bracket 68 can comprise tubular body portion 146 and end flange 148.Tubular body portion 146 can be configured to be accommodated between the spiral winding 86 of hub component 30 and clutch spring 64.End flange 148 can be configured to the axial end portion relatively abutting clutch spring 64 with bracket 62.In the concrete example provided, end flange 148 has surface that directly abut the axial end portion of clutch spring 64, profile twist.Tang slit 150 can be formed in spring bracket 68 and its size can be configured to receive tang 104, thus spring bracket 68 is connected to the second end 90 of clutch spring 64, to rotate thereupon.
Get back to Fig. 2 and Fig. 3, at least one spacer spring 72 described can be accommodated in input queued switches part 70 and export between actuator 74, so that at input queued switches part 70 and export transmitting rotary power between actuator 74.In the example provided, at least one spacer spring 72 described comprises single-screw torsion spring 154, it constantly increases along with the moment of torsion transmitted via it and opens (namely radially expanding), and input queued switches part 70 and output actuator 74 comprise spiral spring groove 160 and actuator protuberance 162 separately.It is to be understood however that, adding or substituting as the single-screw torsion spring 154 described in the illustrated example, other material can be used, such as elastomer (such as rubber, elastic foam), and/or at least one spacer spring 72 described can comprise the one or more springs circumferentially arranged around input hub 20.Helical torsion spring 154 axially can compress between input queued switches part 70 and output actuator 74.In the example provided, helical torsion spring 154 is wound around in the opposite direction along the side be wound around with clutch spring 64, but is understood that other structure is also in the scope of present disclosure.Will also be understood that and alternatively between input queued switches part 70 and output actuator 74, multiple circumferentially separated helical coil springs can be installed.Spiral spring groove 160 is configured to the axial end portion of the correspondence abutting helical torsion spring 154, and actuator protuberance 162 is configured to the axial end 164 be associated abutting the spring thread forming helical torsion spring 154.Input queued switches part 70 can be connected on clutch output link 66 to rotate thereupon.In the concrete example provided, input queued switches part 70 and clutch output link 66 are integrally formed, and clutch output link 66 is axially arranged along the length of helical torsion spring 154.Should be understood that the spiral winding at least partially 86 of clutch spring 64 is located in the mode of the axial overlap of coil at least partially with helical torsion spring 154 by the structure carried out in like fashion.
One or more Sealing can be combined with, with the inside preventing water and/or chip from entering decoupler 10, and/or to be remained in a part for decoupler 10 by oiling agent in decoupler 10.In the example provided, first Sealing 170 is arranged between annular shoulder 32 and clutch output link 66, second Sealing 172 is arranged in and exports between actuator 74 and clutch output link 66, and the 3rd Sealing 174 is arranged in input hub 20 and exports between actuator 74.First Sealing 170, second Sealing 172 and the 3rd Sealing 174 jointly sealing arrange the inner chamber cave of clutch spring 64.Correspondingly, suitable oiling agent can be used---such as, fat, oil or draw fluid---come lubricating screw coil 86 and clutch surface 140.Although second and the 3rd Sealing 172 and 174 be shown as face seal, be understood that and can use any type of Sealing.3rd Sealing 174 can comprise the retaining member in the groove 182 that can be accommodated in and be formed in input hub 20, such as retaining ring 180.Retaining member (such as retaining ring 180) can limit and export the axial motion that actuator 74 leaves input queued switches part 70.
One or more bearing can be used to support input queued switches part 70 relative to input hub 20 and export actuator 74.In the concrete example provided, clutch shaft bearing 190 is arranged between input queued switches part 70 and damper input link 22, and the second bearing 192 is arranged in hub component 30 and exports between actuator 74.Clutch shaft bearing 190 and the second bearing 192 can be any type of bearings, but are thrust-bearings in the concrete example provided.Clutch shaft bearing 190 can comprise annular portion 200 and radial extension 202, annular portion 200 can be configured to the spin axis supporting input queued switches part 70 relative to input hub 20, and radial extension 202 can be configured to limit input queued switches part 70 and axially move along the spin axis of input hub 20 on the direction towards damper input link 22.Similarly, second bearing 192 can comprise annular portion 206 and radial extension 210, annular portion 206 can be accommodated in hub component 30 and to export between the annular collar 208 on actuator 74 and to be configured to support relative to spin axis input hub 20 exports actuator 74, and radial extension 210 can be configured to restriction output actuator 74 and axially move along the spin axis inputting hub 20 on the direction leaving damper input link 22.In the illustrated example, radial extension 210 is described to abutting the 3rd Sealing 174, but be understood that radial extension 210 can contact other structures, such as, contact the retaining ring in groove (not shown) that the flank (not shown) that formed on hub component 30 or contact be accommodated in hub component 30.
Output link 16 can be configured to provide any structure rotating and export, such as belt wheel, gear, sprocket wheel or roller.In the concrete example provided, output link 16 comprises the belt wheel 230 being configured to engage poly Vbelt (Poly-Vbelt).Output link 16 can in any desired manner---such as, multiple bolt and/or one or more soldering point---be rotatably connected to and export on actuator 74.In the example provided, output link 16 comprises annular and installs hub 232, and this annular is installed hub 232 and is accommodated on the axially extended flank 240 of the annular exported on actuator 74.Output link 16 can be aimed at the spin axis exporting actuator 74 by the periphery face of flank 240, and the seal lip 246 of the 3rd Sealing 174 can engage hermetically with the inside circumference face of flank 240.
Be in operation, live axle DS can cause input hub 20 along the corresponding rotation of this preset rotating direction along the rotation of predetermined sense of rotation, makes the spiral winding 86 of clutch spring 64 to engage with clutch surface 140 and rotating power is passed to clutch output link 66.Because input queued switches part 70 is attached to clutch output link 66 rotatably, therefore rotating power can be input to torsional isolator 56 by input queued switches part 70.The rotating power being incorporated into input queued switches part 70 by helical torsion spring 154, export actuator 74 and transmit and to be delivered on output link 16 (namely, allow output link 16 to other device or structure---such as, the poly Vbelt (not shown) in provided concrete example---provide rotating power).Be understood that the moment torsional vibration be associated with the rotating power be delivered in torsional isolator 56 can be decayed to a certain degree by least one spacer spring 72 described.
When the rotating speed along preset rotating direction of output link 16 exceedes the rotating speed of input hub 20, at least one spacer spring 72 described can unload.The device that the torsional load that permission can be provided relatively little is transmitted from output actuator 74 to input queued switches part 70.Output actuator 74 and input queued switches part 70 such as can have two or more the protuberance (not shown)s coordinated promoting rotating power to transmit from output actuator 74 to input queued switches part 70.In the example provided, axial compression on helical torsion spring 154 is enough large, thus allow frictional force (namely in the end of helical torsion spring 154 and input queued switches part 70 and the frictional force that exports between actuator 74) to bear the moment of torsion of moderate level, make output actuator 74 can reverse direction actuation input queued switches part 70(and the clutch output link 66 together with input queued switches part 70 effectively).Tend to cause the spiral winding 86 of clutch spring 64 circumferentially to shrink to the reverse direction actuation of clutch output link 66, clutch spring 64 is disengaged to a certain extent with the clutch surface 140 of clutch output link 66 at least in part, wherein clutch output link 66, input queued switches part 70, export actuator 74 and output link 16 and can surmount (overrun) along preset rotating direction and input hub 20.
When at least one spacer spring 72 described comprises the torsion spring that the spin axis around decoupler 10 is coaxially wound around, by present disclosure, those skilled in the art is appreciated that the spin balancing of decoupler 10 can change along with the change of the torsional load carried by decoupler 10.In order to unbalanced for rotation impact is dropped to minimum, decoupler 10 can be formed as being that rotation is unbalanced when not having spin load to be transmitted by decoupler 10, and when the spin load transmitted by decoupler 10 increases to predetermined size, rotating imbalance can reduce.In other words, decoupler 10 can be configured to when transmitting the spin load of pre-sizing by decoupler 10 is spin balancing.Export actuator 74 relative to input hub 20 rotation can be limited in predetermined scope, this prespecified range has the end points corresponding to the predetermined minimum loading of at least one spacer spring 72 described and the predetermined maximum load of at least one spacer spring 72 described.
Be understood that description is above only exemplary in essence, and be not meant to restriction the present invention and application or purposes.Although describe in the description and illustrate specific example in the accompanying drawings, but those of ordinary skill in the art can understand, various remodeling can be made when not departing from the scope of the present invention limited in claims to the present invention and equivalent substituting will be carried out to element of the present invention.In addition, mixing and the cooperation of characteristic, element and/or function between different examples is imagined clearly at this, make the those of ordinary skill in this field can understand the characteristic of an example, element and/or function from present disclosure can be merged in appropriate circumstances in another example, unless additionally described.In addition, many changes can be made, to make specific situation or material adapt to the instruction of present disclosure when not departing from the base region of present disclosure.Therefore, although contemplate the instruction that best mode is used for performing present disclosure at present, object is that present disclosure is not limited in by the specific example described with specification shown in accompanying drawing, but the scope of present disclosure will be included in any mode of execution in the scope of description above and additional claim.
Element list:
Claims (14)
1. a decoupler, comprising:
Input hub;
Output link; And
Clutch and isolated system, described clutch and isolated system have overrunning clutch and torsional isolator, described overrunning clutch has clutch input structure, clutch spring, bracket and clutch export structure, described clutch input structure is connected in described input hub regularly to rotate together with described input hub, described clutch spring is formed by spring thread and has multiple coil and the first end being installed on described bracket, described bracket is non-rotatably installed on described input hub and is oriented against described clutch input structure by the axial end of the spring thread forming the described first end of described clutch spring, described clutch export structure has clutch surface, wherein, the described coil structure of described clutch spring is for expanding against described clutch surface rotating power is passed to described clutch export structure from described input hub along the first sense of rotation, and, the described coil structure of described clutch spring is for shrinking to allow described clutch export structure to surmount described input hub along described first sense of rotation, described torsional isolator comprises input queued switches part, export actuator and at least one spring, at least one spring construction described is along described first sense of rotation transmitting torque between described input queued switches part and described output actuator, described input queued switches part is connected in described clutch export structure to rotate together with described clutch export structure, described output link is connected in described output actuator to rotate together with described output actuator,
Wherein, at least one layout of spring described of described torsional isolator is at the radial outside of described clutch spring.
2. decoupler according to claim 1, wherein, at least one spring described of described torsional isolator comprises the single-screw torsion spring coaxially installed around described clutch spring.
3. decoupler according to claim 2, wherein, described single-screw torsion spring and described clutch spring are wound around along contrary direction.
4. decoupler according to claim 1, wherein, described overrunning clutch also comprises spring bracket, and described spring bracket comprises the body portion between described coil and described input hub being accommodated in described clutch spring, and described spring bracket can rotate relative to described input hub.
5. decoupler according to claim 4, wherein, described clutch spring also comprises the second end relative with described first end, and described the second end has the tang being mounted to described spring bracket.
6. decoupler according to claim 1, also comprises sealing system, and described sealing system seals the cave, chamber arranging described clutch spring in described clutch and isolated system.
7. decoupler according to claim 6, wherein, receives oiling agent in cave, described chamber.
8. decoupler according to claim 6, wherein, described sealing system comprises at least one face seal.
9. decoupler according to claim 1, wherein, described bracket is limited with groove, the described first end of described clutch spring is incorporated in described groove, further, described overrunning clutch also comprises support member, and described support member is connected in described input hub regularly, described support member abuts the described first end of described clutch spring, thus stops described first end to be deviate from from described groove.
10. decoupler according to claim 9, wherein, described support member is press-fitted on described input hub.
11. decouplers according to claim 1, wherein, when not having spin load to be transmitted by described decoupler, described decoupler rotates uneven, further, when the spin load transmitted by described decoupler increases to predetermined size, the rotation imbalance of described decoupler reduces.
12. decouplers according to claim 1, wherein, described output actuator be limited in prespecified range relative to the rotation of described input hub, described prespecified range has the end points corresponding with the predetermined maximum load of at least one spring described in the predetermined minimum loading of at least one spring described in described torsional isolator and described torsional isolator.
13. decouplers according to claim 1, also comprise the damper being mounted to described input hub.
14. decouplers according to claim 1, wherein, described clutch input structure comprises barrel surface, and in the vertical center line of described spring thread the forming described clutch spring position crossing with described axial end, the described vertical center line of the described spring thread of position that intersects relative to described vertical center line and the described axial end at described spring thread of the center line of described barrel surface that obtains of the described vertical center line that is parallel to described spring thread arranges radially outwardly.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US35854010P | 2010-06-25 | 2010-06-25 | |
| US61/358,540 | 2010-06-25 | ||
| PCT/CA2011/000726 WO2011160208A1 (en) | 2010-06-25 | 2011-06-22 | Isolation pulley with overrunning and vibration damping capabilities |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102959262A CN102959262A (en) | 2013-03-06 |
| CN102959262B true CN102959262B (en) | 2016-01-20 |
Family
ID=45370782
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180031578.8A Active CN102959262B (en) | 2010-06-25 | 2011-06-22 | There is the isolation belt wheel of the ability of surmounting and vibration damping ability |
Country Status (8)
| Country | Link |
|---|---|
| US (2) | US9989103B2 (en) |
| EP (1) | EP2585727A4 (en) |
| JP (1) | JP2013533439A (en) |
| KR (1) | KR20130108516A (en) |
| CN (1) | CN102959262B (en) |
| BR (1) | BR112012029750A2 (en) |
| CA (1) | CA2829076A1 (en) |
| WO (1) | WO2011160208A1 (en) |
Families Citing this family (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20100095947A1 (en) | 2008-10-20 | 2010-04-22 | David Gellis | Hand warmer |
| WO2012079155A1 (en) * | 2010-12-16 | 2012-06-21 | Litens Automotive Partnership | Clutched driven device |
| US8506434B2 (en) * | 2011-01-24 | 2013-08-13 | The Gates Corporation | Isolating decoupler |
| USRE47143E1 (en) | 2011-08-08 | 2018-11-27 | Litens Automotive Partnership | Decoupler assembly |
| DE102013206444B4 (en) | 2012-04-24 | 2022-05-25 | Schaeffler Technologies AG & Co. KG | drive wheel |
| US8888622B2 (en) * | 2012-06-04 | 2014-11-18 | The Gates Corporation | Isolator decoupler |
| WO2014022912A1 (en) | 2012-08-07 | 2014-02-13 | Litens Automotive Partnership | Decoupler carrier with balanced forces |
| CN102817936B (en) * | 2012-09-05 | 2015-06-03 | 李志敏 | Spring friction clutch mechanism for belt pulley and one-way coupling damping belt pulley |
| BR102012022803B1 (en) * | 2012-09-10 | 2017-05-02 | Zen S/A Indústria Metalúrgica | decoupler with freewheel system and vibration damping |
| US11236812B2 (en) * | 2012-09-10 | 2022-02-01 | Zen S/A Industria Metalurgica | Decoupler with one-way clutch and fail-safe system |
| WO2014113862A1 (en) | 2013-01-25 | 2014-07-31 | Litens Automotive Partnership | Clutched device with wrap spring clutch with overrun locking member |
| EP2827014A1 (en) * | 2013-07-17 | 2015-01-21 | Volvo Car Corporation | Decoupler NVH seal |
| CN105556148B (en) * | 2013-08-27 | 2019-03-26 | 利滕斯汽车合伙公司 | Isolator used in the engine for being assisted or being started by endless drive component as motor generator unit or motor |
| US9097297B1 (en) * | 2014-01-17 | 2015-08-04 | Gates Corporation | Hydraulic isolator decoupler |
| US9546709B2 (en) | 2014-09-10 | 2017-01-17 | Gates Corporation | Crankshaft isolating pulley |
| CN107002767A (en) * | 2014-12-09 | 2017-08-01 | 利滕斯汽车合伙公司 | Isolator used in the engine for being aided in or being started by endless drive component as MGU or motor |
| US9291253B1 (en) | 2015-03-24 | 2016-03-22 | Gates Corporation | Isolating decoupler |
| US9759266B1 (en) * | 2016-05-13 | 2017-09-12 | Gates Corporation | Isolating decoupler |
| DE102016211558B4 (en) | 2016-06-28 | 2019-01-31 | Schaeffler Technologies AG & Co. KG | Riemenscheibenentkoppler |
| DE102016216274B4 (en) * | 2016-08-30 | 2018-08-02 | Schaeffler Technologies AG & Co. KG | Pulley decoupler with double hub |
| KR101765645B1 (en) * | 2016-10-24 | 2017-08-07 | 현대자동차 주식회사 | Motor coupling structure of engine clutch for hybrid transmission |
| CN108253086A (en) * | 2018-01-26 | 2018-07-06 | 淄博职业学院 | A kind of automobile mechanical slides damping drag-reduction energy-saving device |
| US11549558B2 (en) | 2018-08-01 | 2023-01-10 | Gates Corporation | Isolator decoupler |
| US11732774B2 (en) * | 2018-09-10 | 2023-08-22 | Litens Automotive Partnership | Combined isolation and torsional vibration damping device |
| US10807460B2 (en) * | 2019-03-13 | 2020-10-20 | GM Global Technology Operations LLC | Method of controlling a powertrain system of a vehicle |
| US12005779B2 (en) * | 2019-03-26 | 2024-06-11 | Litens Automotive Partnership | Rotary device with clutch with time-based slip and method of providing time-based slip for a rotary device |
| US11879536B2 (en) | 2019-08-20 | 2024-01-23 | Litens Automotive Partnership | Rotary device with chambered member and method of making same |
| DE212020000778U1 (en) * | 2019-12-09 | 2022-09-07 | American Axle & Manufacturing, Inc. | Dampened isolation pulley with electro-adhesive clutch |
| IT202000009295A1 (en) * | 2020-04-28 | 2021-10-28 | Dayco Europe Srl | IMPROVED FILTER PULLEY, SYSTEM INCLUDING SUCH PULLEY AND RELATED CONTROL METHOD |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1668859A (en) * | 2002-07-26 | 2005-09-14 | 利滕斯汽车公司 | Overrunning alternator decoupler pulley with bare wire spring and grease lubrication |
| WO2007003052A1 (en) * | 2005-07-05 | 2007-01-11 | Litens Automotive Partnership | Overrunning decoupler with locking mechanism |
Family Cites Families (34)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2534033A (en) | 1941-02-20 | 1950-12-12 | Chrysler Corp | Clutch |
| GB883608A (en) | 1960-03-03 | 1961-12-06 | Normalair Ltd | Improvements relating to clutches |
| US5044943A (en) | 1990-08-16 | 1991-09-03 | Applied Materials, Inc. | Spoked susceptor support for enhanced thermal uniformity of susceptor in semiconductor wafer processing apparatus |
| US5139463A (en) | 1991-06-05 | 1992-08-18 | Litens Automotive Partnership | Serpentine drive with coil spring alternator connection |
| US5156573A (en) | 1991-06-05 | 1992-10-20 | Litens Automotive Partnership | Serpentine drive with coil spring-one-way clutch alternator connection |
| JP2761191B2 (en) | 1994-08-12 | 1998-06-04 | バンドー化学株式会社 | Belt transmission method and belt transmission device |
| DE781906T1 (en) | 1994-09-14 | 1997-11-20 | Bando Chemical Ind | DEVICE FOR DRIVING AN AC POWER MACHINE, AND AC POWER GENERATOR FOR MACHINE ACCESSORIES USED THEREFOR |
| GB9420741D0 (en) | 1994-10-14 | 1994-11-30 | Litens Automotive Inc | Crankshaft decoupler |
| US5722909A (en) | 1995-09-27 | 1998-03-03 | Litens Automotive Partnership | Series type decoupling device |
| EP0980479B1 (en) | 1997-05-07 | 2003-08-27 | Litens Automotive Partnership | Serpentine drive system with improved over-running alternator decoupler |
| US6394248B1 (en) | 2000-05-31 | 2002-05-28 | Ntn Corporation | Compression spring complaint one-way over-running clutch pulley |
| JP2002227973A (en) * | 2001-02-05 | 2002-08-14 | Ntn Corp | Spring clutch |
| BR0214737B1 (en) | 2001-12-05 | 2011-02-22 | belt tensioner and rotary apparatus for selectively transmitting torque or rotational power. | |
| US7153227B2 (en) | 2002-04-18 | 2006-12-26 | Litens Automotive | Isolator for alternator pulley |
| AU2003232546A1 (en) | 2002-06-10 | 2003-12-22 | Litens Automotive | Overrunning enabled automotive starter/generator |
| CA2759773C (en) | 2002-11-22 | 2013-05-28 | Litens Automotive | Flexible coupling with misalignment compensation |
| PL210159B1 (en) | 2003-02-04 | 2011-12-30 | Litens Automotive | Crankshaft torque modulator |
| CN100513816C (en) | 2003-09-22 | 2009-07-15 | 利滕斯汽车合伙公司 | Crankshaft decoupler |
| CA2547383C (en) | 2003-12-09 | 2013-08-13 | Litens Automotive Partnership | Spring travel limiter for overrunning alternator decoupler |
| CA2596734C (en) | 2005-02-03 | 2013-12-03 | Litens Automotive Partnership | Torque limited decoupler |
| KR101396075B1 (en) | 2006-04-26 | 2014-05-16 | 리텐스 오토모티브 파트너쉽 | One-way isolator for high torque devices |
| DE102007047393A1 (en) | 2006-10-26 | 2008-04-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torsion vibration damper e.g. dual mass flywheel, for internal combustion engine, has coupler with spring connected with ring units, where ring units are connected with flywheels and end of spring is radially supported at ring units |
| DE102007047394A1 (en) | 2006-10-26 | 2008-04-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torsional vibration damper for internal combustion engine, has loop spring unit whose end is connected rotatably with ring that comprises support regions for energy storages and/or control regions for free-wheeling effect |
| US8479847B2 (en) | 2007-10-23 | 2013-07-09 | GM Global Technology Operations LLC | Breakaway clutch for controllable speed accessory drive system |
| US8944947B2 (en) * | 2008-03-26 | 2015-02-03 | Jtekt Corporation | Pulley unit |
| JP5677305B2 (en) | 2008-10-27 | 2015-02-25 | リテンズ オートモーティヴ パートナーシップ | How to make an overrunning decoupler |
| US8485331B2 (en) * | 2008-11-17 | 2013-07-16 | Litens Automotive Partnership | Driven accessory with low-power clutch for activating or de-activating same |
| BRPI1009789A2 (en) | 2009-03-03 | 2016-08-23 | Litens Automotive Inc | uncoupler. |
| US9068608B2 (en) * | 2009-09-17 | 2015-06-30 | Gates Corporation | Isolator decoupler |
| EP2513453A1 (en) | 2009-12-16 | 2012-10-24 | Litens Automotive Partnership | Device with integrated decoupler |
| CA2798096A1 (en) | 2010-05-25 | 2011-12-01 | Litens Automotive Partnership | Decoupler assembly with sliding interface between hub and pulley |
| CN103140693B (en) * | 2010-06-25 | 2015-11-25 | 利滕斯汽车合伙公司 | There is the separator of integrated torshional vibration damper |
| US8678157B2 (en) * | 2011-05-25 | 2014-03-25 | Gates Corporation | Isolator decoupler |
| US8813928B2 (en) * | 2011-10-14 | 2014-08-26 | The Gates Corporation | Alternator isolating decoupler |
-
2011
- 2011-06-22 BR BR112012029750A patent/BR112012029750A2/en not_active Application Discontinuation
- 2011-06-22 KR KR1020127033630A patent/KR20130108516A/en not_active Withdrawn
- 2011-06-22 US US13/805,085 patent/US9989103B2/en active Active
- 2011-06-22 WO PCT/CA2011/000726 patent/WO2011160208A1/en active Application Filing
- 2011-06-22 EP EP11797419.6A patent/EP2585727A4/en not_active Withdrawn
- 2011-06-22 CN CN201180031578.8A patent/CN102959262B/en active Active
- 2011-06-22 JP JP2013515644A patent/JP2013533439A/en active Pending
- 2011-06-22 CA CA2829076A patent/CA2829076A1/en not_active Abandoned
-
2018
- 2018-01-17 US US15/873,807 patent/US10663008B2/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1668859A (en) * | 2002-07-26 | 2005-09-14 | 利滕斯汽车公司 | Overrunning alternator decoupler pulley with bare wire spring and grease lubrication |
| WO2007003052A1 (en) * | 2005-07-05 | 2007-01-11 | Litens Automotive Partnership | Overrunning decoupler with locking mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013533439A (en) | 2013-08-22 |
| CN102959262A (en) | 2013-03-06 |
| EP2585727A4 (en) | 2018-03-28 |
| US20180142738A1 (en) | 2018-05-24 |
| BR112012029750A2 (en) | 2016-08-09 |
| CA2829076A1 (en) | 2011-12-29 |
| US9989103B2 (en) | 2018-06-05 |
| KR20130108516A (en) | 2013-10-04 |
| EP2585727A1 (en) | 2013-05-01 |
| WO2011160208A1 (en) | 2011-12-29 |
| US10663008B2 (en) | 2020-05-26 |
| US20130087428A1 (en) | 2013-04-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102959262B (en) | There is the isolation belt wheel of the ability of surmounting and vibration damping ability | |
| JP5677305B2 (en) | How to make an overrunning decoupler | |
| CN102341610B (en) | Decoupler featuring helical wrap clutch spring and coil damper springs | |
| CN107429816B (en) | Filter belt wheel | |
| CN102985716B (en) | Overrunning decoupler | |
| US9638308B2 (en) | Pulley structure | |
| US9033832B1 (en) | Isolating decoupler | |
| CN107923479A (en) | Clutch disc with centrifugal force pendulum | |
| KR101561400B1 (en) | Torsional oscillation damping device | |
| US20130324335A1 (en) | Isolator Decoupler | |
| CN101210589B (en) | Driving wheel | |
| EP1390633B1 (en) | Device for isolating torque fluctuations | |
| US9964177B2 (en) | Dual mass flywheel | |
| CN105518337A (en) | Damper unit and starting device | |
| JP2016505124A (en) | Elastic joint | |
| US10400873B2 (en) | Torsional vibration damper | |
| CN103453071A (en) | Hub device for a torsional vibration damper and corresponding torsional vibration damper | |
| CN103180635A (en) | Centrifugal force pendulum device | |
| US20220213954A1 (en) | Decoupler | |
| JP6839994B2 (en) | Torque fluctuation absorption damper | |
| CN114303015A (en) | Pulley Decoupler | |
| JP2016008660A (en) | Constant velocity joint | |
| CN107250612B (en) | Tensioner with improved damping device | |
| JP2003161352A (en) | Planetary roller speed changer | |
| JP2008144827A (en) | Pulley with damper |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |